Valve with sync cam

ABSTRACT

Valves include a valve body having an inner surface and an outer surface, the inner surface and the outer surface defining an inlet, an outlet, and a body cavity between the inlet and the outlet; a gate movably coupled to the valve body and moveable over a portion of the valve body at least partially between the inlet and the outlet, the gate including a cam stop; and a drive assembly, the drive assembly including a drive shaft and a sync cam, the sync cam of the drive assembly movably positioned on the drive shaft and slidably positioned relative to the cam stop.

TECHNICAL FIELD

This disclosure relates to valves. More specifically, this disclosurerelates to sync cams used in valves.

BACKGROUND

Valve elements are used to regulate or control the flow of material byopening, closing, or partially obstructing various passageways. One typeof valve is a sleeve valve, which can be used in a number ofapplications. Some sleeve valves contain one or more perforated openingson a sleeve that allow for material to flow through the valve. Anothertype of valve is a fixed cone valve. Some fixed cone valves include acone that may contact a gate to restrict material from flowing throughthe valve.

SUMMARY

Disclosed is a valve including a valve body having an inner surface andan outer surface, the inner surface and the outer surface defining aninlet, an outlet, and a body cavity between the inlet and the outlet; agate movably coupled to the valve body and moveable over a portion ofthe valve body at least partially between the inlet and the outlet, thegate including a cam stop; and a drive assembly, the drive assemblyincluding a drive shaft and a sync cam, the sync cam of the driveassembly movably positioned on the drive shaft and slidably positionedrelative to the cam stop.

Also disclosed is a method for syncing a sleeve valve includingaccessing a valve including a valve body having an inner surface and anouter surface, the inner surface and the outer surface defining aninlet, an outlet, and a body cavity between the inlet and the outlet; agate coupled to the valve body and moveable over a portion of the valvebody at least partially between the inlet and the outlet, the gateincluding a first cam stop and a second cam stop; and a drive assembly,the drive assembly including a first sync cam movably coupled to a firstdrive shaft and a second sync cam movably coupled to a second driveshaft, the first sync cam slidably positioned relative to the first camstop, the second sync cam slidably positioned relative to the second camstop, the first sync cam including a first front flange and a first backflange, the second sync cam including a second front flange and a secondback flange; moving the gate to a front stop position, wherein the frontstop position includes at least one of the first front flange and thesecond front flange in contact with at least one of the first cam stopand the second cam stop; aligning the first front flange in the frontstop position to contact the first cam stop and the second front flangein the front stop position to contact the second cam stop; moving thegate to a back stop position, wherein the back stop position includes atleast one of the first back flange and the second back flange in contactwith at least one of the first cam stop and the second cam stop; andaligning the first back flange in the back stop position to contact thefirst cam stop and the second back flange in the back stop position tocontact the second cam stop.

Also disclosed is a method of controlling the flow of fluid in a pipesystem including controlling a valve in the pipe system, the valveincluding a valve body having an inner surface and an outer surface, theinner surface and the outer surface defining an inlet, an outlet, and abody cavity between the inlet and the outlet; a gate movably coupled tothe valve body and moveable over a portion of the valve body at leastpartially between the inlet and the outlet, the gate including a camstop; and a drive assembly, the drive assembly including a drive shaftand a sync cam on the drive shaft, the sync cam of the drive assemblyincluding a front flange and a back flange, the sync cam movablypositioned on the drive shaft of the drive assembly and slidablypositioned relative to the at least one cam stop, a first gap definedbetween the front flange and the at least one cam stop, a second gapbetween a back flange and the at least one cam stop; moving the sync camin a first direction to a front stop position, wherein the front stopposition reduces the first gap; and moving the gate in the firstdirection to allow fluid to flow from the inlet to the outlet.

Various implementations described in the present disclosure may includeadditional systems, methods, features, and advantages, which may notnecessarily be expressly disclosed herein but will be apparent to one ofordinary skill in the art upon examination of the following detaileddescription and accompanying drawings. It is intended that all suchsystems, methods, features, and advantages be included within thepresent disclosure and protected by the accompanying claims.

BRIEF DESCRIPTION OF THE DRAWINGS

The features and components of the following figures are illustrated toemphasize the general principles of the present disclosure.Corresponding features and components throughout the figures may bedesignated by matching reference characters for the sake of consistencyand clarity.

FIG. 1 is a perspective view of a sleeve valve in accord with oneembodiment of the current disclosure.

FIG. 2 is a perspective view from another end of the sleeve valve ofFIG. 1.

FIG. 3 is a cross-sectional view of the sleeve valve of FIG. 1.

FIG. 4A is a detail view of a sync cam, a drive shaft, and a gate of thesleeve valve of FIG. 3.

FIG. 4B is a cross-sectional view of the sync cam, drive shaft, and gateof the sleeve valve of FIG. 3.

FIG. 5 is a top view of the sync cam of the sleeve valve of FIG. 1.

FIG. 6 is a cross-sectional view of the sync cam of FIG. 5 taken alongline 6-6.

FIG. 7 is a detail view of the sync cam, drive shaft, and gate of thesleeve valve of FIG. 1.

FIG. 8A is a side view of a pair of drive lines of a drive assembly andthe gate surrounding a sleeve of the sleeve valve of FIG. 1, wherein theview of a drive shaft of each drive lines is abridged, showing only aportion of the drive shaft.

FIG. 8B is a top view of the gate and one of the drive lines of FIG. 8.

FIG. 9A is a side view of a front direction load balancing screw of thesync cam of FIG. 5. In the current embodiment the front direction loadbalancing screw is identical to a backward direction load balancingscrew.

FIG. 9B is a top view of the front direction load balancing screw ofFIG. 9A. In the current embodiment the front direction load balancingscrew is identical to the backward direction load balancing screw.

FIG. 10 is a cross-sectional view of the interior of the body cavityportion of the valve body of FIG. 1 including the drive line, gate, andsleeve valve, including an actuator located on an exterior of the sleevevalve.

FIG. 11 is a side view of the drive line including the drive shaft, thesync cam, and the actuator located on an exterior of the sleeve valve,wherein the view of the drive shaft is abridged, showing only the frontportion and the back portion of the drive shaft.

FIGS. 12A and 12B are perspective detail views of the drive line andgate of FIG. 10 and show the sync cam in a first position and a secondposition on the drive shaft, respectively.

FIGS. 13A, 13B, 13C, 13D, and 13E show a side view of the drive assemblyand gate of FIG. 12 and show a method for syncing the sleeve valve.

FIGS. 14A, 14B, 14C, 14D, and 14E show a side view of the drive assemblyand gate of FIG. 12 and show a method for controlling the flow of fluidthrough the sleeve valve.

FIG. 15 is a perspective view of a fixed cone valve in accord with oneembodiment of the current disclosure.

FIG. 16 is a perspective view from another end of the fixed cone valveof FIG. 15 with a hood of the fixed cone valve removed.

FIG. 17 is a perspective view from another end of the fixed cone valveof FIG. 15 with the hood of the fixed cone valve included.

FIG. 18 is a cross-sectional view of the fixed cone valve of FIG. 15.

FIG. 19 is a cross-sectional detail view of the fixed cone valve of FIG.15 including a drive line and a gate, including an actuator located onan exterior of the fixed cone valve.

DETAILED DESCRIPTION

Disclosed is a valve and associated methods, systems, devices, andvarious apparatus. The valve includes a drive assembly having at leastone drive line including a sync cam and a drive shaft. It would beunderstood by one of skill in the art that the disclosed valve isdescribed in but a few exemplary embodiments among many. No particularterminology or description should be considered limiting on thedisclosure or the scope of any claims issuing therefrom.

One embodiment of a valve of the present invention is a sleeve valve100, which is disclosed and described in FIGS. 1-2. In FIG. 1 the sleevevalve 100 includes a valve body 110 that has an inner surface 117 (shownin FIG. 3) and an outer surface 119. The inner surface 117 and the outersurface 119, as illustrated in the current embodiment, define an inletportion 120, an outlet portion 130, and a body cavity portion 140. Inthe current embodiment, the inlet portion 120 defines an inlet 125 andis conical-shaped and welded to the body cavity portion 140, althoughother joining interfaces are contemplated by this disclosure and shouldbe considered included. The outlet portion 130 defines an outlet 135.The outlet portion 130 and the body cavity portion 140, in the currentembodiment, are both of an approximately cylindrical shape. The shape ofthe inlet portion 120, the outlet portion 130, and the body cavityportion 140 are not limiting and may be other shapes. The inlet portion120, the outlet portion 130, and the body cavity portion 140 in thecurrent embodiment are made of welded fabricated carbon steel plates,although one of skill in the art would recognize that other materialscould be used and such a disclosure is not limiting. The inlet portion120, the outlet portion 130, and the body cavity portion 140 may alsoinclude flanged ends, and as seen in the current embodiment in FIG. 1,the inlet portion 120 includes one flanged end 124 on the opposite endof that which is connected to the body cavity portion 140. Also, in thecurrent embodiment, both ends of the outlet portion 130 include flangedends 132 and 134, and the end of the body cavity portion 140 that facesthe outlet portion 130 includes a flanged end 142.

The current embodiment includes fastening elements 141 in the form of aplurality of nuts and bolts coupling the flanged end 142 of the bodycavity portion 140 to the flanged end 134 of the outlet portion 130 andthereby joining the body cavity portion 140 to the outlet portion 130.However, various types of fasteners, such as nails, screws, welding, orany other type of fastener may be used, and the disclosure of nuts andbolts is not limiting upon the fastener that must be used. Additionally,as illustrated in FIG. 1, the sleeve valve 100 includes a drive assembly170 including an actuator motor 175 and drive lines (330 and 340 in FIG.3). Further, the current embodiment of the sleeve valve 100 includesinspection ports 190 a and 190 b that are circular and defined in thebody cavity portion 140 and include inspection lids 195 a,b fastened tothe outer surface 119 of the valve body 110 via a plurality of nuts andbolts. However, various types of fasteners, such as nails, screws, orany other type of fastener may be used, and the disclosure of nuts andbolts is not limiting upon the fastener that must be used. The shape ofthe inspection ports 190 a and 190 b is not limiting, and other shapessuch as oval and square may be used. The inspection ports 190 a and 190b allow access to the interior of the body cavity portion 140. In thecurrent embodiment, inspection ports 190 a,b include hinges 191 a,b andhandles 192 a,b (192 b not shown).

The current embodiment of the sleeve valve 100 also includes an accessport 194 that is circular and defined on the outer surface 119 of thevalve body 110. The access port 194 includes an access lid 196 fastenedto the outer surface 119 of the valve body 110 via a plurality of nutsand bolts. However, various types of fasteners, such as nails, screws,or any other type of fastener may be used, and the disclosure of nutsand bolts is not limiting upon the fastener that must be used. Moreover,the shape of the access port 194 is not limiting and other shapes suchas oval and square may be used. In the current embodiment, the bodycavity portion 140 and the outlet portion 130 include pressure gauges185 a and 185 b that are located on the outer surface 119, but these arenot required for all embodiments.

FIG. 2 displays a perspective view of the sleeve valve 100 where theoutlet portion 130 is in the foreground of the illustration. As can beseen in the current embodiment, the actuator motor 175 is mounted to theouter surface 119 of the flanged end 134 of the outlet portion 130,although the actuator motor 175 may be mounted to any portion of thesleeve valve 100. The actuator motor 175 is connected to the drive lines(330 and 340 in FIG. 3) by a splitter 274, or three-way gear, and twoactuator drive shafts 276 a and 276 b extending from the splitter 274 totwo separate machine screw actuators 278 a and 278 b, where actuatordrive shaft 276 a is attached to machine screw actuator 278 a andactuator drive shaft 276 b is attached to machine screw actuator 278 b.Splitter 274 translates rotational movement from the actuator motor 175to the actuator drive shafts 276 a,b, which translate rotationalmovement to each machine screw actuator 278 a,b, respectively. Machinescrew actuator 278 a is part of drive line 330 and machine screwactuator 278 b is part of drive line 340. In the current embodiment, themachine screw actuators 278 a and 278 b are Duff-Norton Machine ScrewActuators, model number DM-9006; however, one of skill in the art wouldrecognize that such a disclosure is not limiting and other types ofmachines or operations that enable the drive shaft 332 and/or 342(described with reference to FIG. 3) to operate may be used. The driveassembly 170 can be operated in many different ways, includingautomatically from a remote location, via local controls on the actuatormotor 175 itself, or via a clutch lever, and the methods of operation ofthe drive assembly 170 are not intended to be limiting. The actuatormotor 175 is an electric motor, but may also be a manual handwheel inalternative embodiments. Additionally, in the current embodiment,actuator spacers 279 a,b,c,d (279 d not shown) mount machine screwactuator 278 a to the outlet portion 130 and actuator spacers 279e,f,g,h (279 h not shown) mount machine screw actuator 278 b to theoutlet portion 130, but the machine screw actuators 278 a,b may bemounted to the outlet portion 130 by any other types or amount offasteners.

FIG. 3 provides a cross-sectional view of the sleeve valve 100. In thecurrent embodiment, material flows from the inlet portion 120 through abody cavity defined within the body cavity portion 140 to the outletportion 130. Inspection port 190 a and access port 194 are also shown inthe current embodiment. In the current embodiment, the valve body 110includes a sleeve 310 located within the body cavity portion 140 andsecured at a sleeve flanged end 312 to the outlet portion 130 by aplurality of nuts and bolts. The sleeve 310, in the current embodiment,is cylindrically shaped with a dome-shaped sleeve end 311 that preventsmaterial from entering the sleeve 310 from sleeve end 311. The sleeveflanged end 312 is open to allow material to flow freely from the sleeve310 to the outlet portion 130 once the material enters the interior ofthe sleeve 310. The shapes of sleeve end 311 and sleeve flanged end 312are not limiting and other shapes may be used. Additionally, thetechnique of securing sleeve flanged end 312 of sleeve 310 to the outletportion 130 may be achieved using any known technique in the art. Thesleeve 310 in the current embodiment is made of a welded fabricatedstainless steel plate, although one of skill in the art would recognizethat other materials could be used and such a disclosure is notlimiting.

In the current embodiment, sleeve 310 includes perforated openings 315,which allow material to flow from the body cavity portion 140 to theinterior of the sleeve 310. Although multiple perforated openings 315are shown in the current embodiment, only one perforated opening may beincluded, and any number of perforated openings 315 may be included invarious embodiments. In the current embodiment, perforated openings 315refer to all openings in the sleeve 310. The elements to which reference315 points are exemplary only and should not be considered limiting onthe disclosure. Proximate to the sleeve 310, in the current embodiment,is a gate 320, which is moveable over a portion of the sleeve 310including at least one of the perforated openings 315. When the gate320, in the current embodiment, is positioned over at least one of theperforated openings 315, the gate 320 prevents material from flowinginto or out of the interior of the sleeve 310 through the at least oneperforated opening 315 that the gate 320 is positioned over. However,neither the material nor shape of the gate 320 is limiting, and variousmaterials or shapes may be used in various embodiments. The gate 320 inthe current embodiment is made of a welded fabricated stainless steelplate, although one of skill in the art would recognize that othermaterials could be used and such a disclosure is not limiting. As can beseen in FIG. 3, the current embodiment includes drive line 330, whichoperates to move the gate 320 axially over the sleeve 310. In thecurrent embodiment, the drive line 330 includes a drive shaft 332, whichis a cylindrical rod that rotates and includes at least a threadedportion. The drive shaft 332 connects to the machine screw actuator 278a in the current embodiment.

The drive shaft 332 in the current embodiment is made of stainlesssteel, although one of skill in the art would recognize that othermaterials could be used and such a disclosure is not limiting. The gate320 will be enabled to move axially along the sleeve 310 within theportion of the drive shaft 332 that is threaded. Moreover, in thecurrent embodiment, the drive line 330 includes a sync cam 334, which ismoveably positioned around the drive shaft 332. Additionally, when thedrive shaft 332 rotates the sync cam 334 may move axially relative to acam stop 326 in the form of a stop plate, though other cam stops may beused in other embodiments.

In addition, the sync cam 334 in the current embodiment includes a frontflange 327 and a back flange 329. The front flange 327 includes twoforward direction load balancing screws 335 a and 335 b (335 b shown inFIG. 4A). Although the current embodiment includes two forward directionload balancing screws 335 a and 335 b, other embodiments may include anynumber of forward direction load balancing mechanisms, which can be nutsand bolts, screws, other types of fasteners, or any other load balancingmechanism. Additionally, the drive line 330 may include more than onesync cam 334 and drive shaft 332. In the current embodiment, the camstop 326 is connected to and formed on the gate 320, but it is not arequirement that the cam stop 326 be connected to or formed on the gate320.

The cam stop 326 can be a plate or any other mechanism that limitsmovement of the sync cam 334 along the drive shaft 332 relative to thegate 320. Additionally, in the current embodiment, the back flange 329includes three backward direction load balancing screws 368 a,b,c (shownin FIGS. 4A, 4B, 5, and 7); however, this configuration is not meant tobe limiting in terms of the type of mechanism used for backwarddirection load balancing and the number of backward direction loadbalancing mechanisms. The back flange 329 includes at least one backwarddirection load balancing mechanism, which can be achieved with nuts andbolts, screws, other types of fasteners, or any other load balancingmechanism which is known in the art.

The components of the drive line 330, in the current embodiment, are notmeant to be limiting. Additional components may be added to the driveline 330 and the components in combination described above are not allrequired. In the current embodiment, an additional drive line 340 isprovided, although it is not required, and is located approximately 180degrees from drive line 330, though the drive line 340 may be locatedrelative to the drive line 330 in any position in other embodiments.Drive line 340, in the current embodiment, is configured in the same waydrive line 330 is configured. The drive line 340 includes a drive shaft342, which is configured in the same way as drive shaft 332. The driveshaft 342 connects to the machine screw actuator 278 b in the currentembodiment. The drive line 340 also includes a sync cam 344, which isconfigured in the same way as sync cam 334, and the drive line 340 mayinclude more than one sync cam 344 and drive shaft 342. Also, the synccam 344 in the current embodiment includes a front flange 347 and a backflange 349. The front flange 347 includes two forward direction loadbalancing screws 345 a,b (345 a shown in FIG. 8). Although the currentembodiment includes two forward direction load balancing screws 345 a,b,that is not meant to be limiting. The sync cam 344 includes at least oneforward direction load balancing mechanism, which can be achieved withnuts and bolts, screws, other types of fasteners, or any other loadbalancing mechanism.

In the current embodiment, a cam stop 346 is connected to and formed onthe gate 320, but it is not a requirement in all embodiments that thecam stop 346 be connected to or formed on the gate 320. The cam stop 346can be a plate or any other mechanism that limits movement of the synccam 344 along the drive shaft 342 relative to the gate 320.Additionally, in the current embodiment, the back flange 349 includesthree backward direction load balancing screws 378 a,b,c (378 a,c shownin FIG. 8A, 378 b not shown); however, this configuration is not meantto be limiting in terms of the type of mechanism used for backwarddirection load balancing and the number of backward direction loadbalancing mechanisms. The back flange 349 includes at least one backwarddirection load balancing mechanism, which can be achieved with nuts andbolts, screws, other types of fasteners, or any other load balancingmechanism which is known in the art. Although in the current embodimentthe drive line 340 is configured in the same way and includes all of thesame components as drive line 330, the embodiment is not meant to belimiting. Drive line 340 may also include additional components, and thecomponents in combination described above are not all required.Moreover, additional drive lines may be implemented with the sleevevalve 100.

FIG. 4A is a side detail view of the sync cam 334, the drive shaft 332,and the gate 320 of the sleeve valve 100. The drive line 340 isconfigured substantially the same as drive line 330 in the currentembodiment. The sync cam 334, in the current embodiment, includes thefront flange 327, the back flange 329, and a cylindrical middle portion410 extending between the front flange 327 and the back flange 329 andthrough the cam stop 326, although the components of the sync cam 334are not critical. In the current embodiment, the sync cam 334 includestwo forward direction load balancing screws 335 a and 335 b. Eachforward direction load balancing screw 335 a,b extends through the frontflange 327 and through front nuts 435 a,b (435 b shown in FIG. 5),respectively, to contact gate 320. The front flange 327 is coupled tothe middle portion 410 by flange screws 415 a,b,c,d (415 c,d shown inFIG. 4B). In alternative embodiments, the front flange 327 may becoupled to the middle portion 410 by other fastening methods, includinggluing or welding, or the front flange 327 may be formed on the middleportion 410 so that the sync cam 334 is a single unit. The back flange329 is formed on the middle portion 410 so that the middle portion 410and back flange 329 are a single unit, though the back flange 329 may beseparate from the middle portion 410 in other embodiments. The backflange 329 may be coupled to the middle portion 410 by screws, welding,or gluing in other embodiments. Backward direction load-balancing screws368 a,b,c extend through back flange 329.

FIG. 4B is a side cross-sectional detail view of the sync cam 334, thedrive shaft 332, the gate 320, and the sleeve 310 of the sleeve valve100. In the current embodiment, the gate 320 is located proximate to thesleeve 310, and as seen in FIG. 14, there is nearly no space betweengate 320 and sleeve 310, although there may be space in variousembodiments. Sync cam 334, in the current embodiment, also defines acircular drive shaft bore 416 through the center of the sync cam 334,including through front flange 327, middle portion 410, and back flange329, although the position and shape of the bore is not critical. Thedrive shaft bore 416 is threaded in the current embodiment such that thethreads of drive shaft bore 416 engage threads of drive shaft 332 toallow movement of the sync cam 334 along the drive shaft 332, though thedrive shaft 332 may engage the sync cam 334 in any manner in otherembodiments to allow movement of the sync cam 334 along the drive shaft332. Because the sync cam 334 engages the drive shaft 332, the sync cam334 is thereby moveably positioned relative to the drive shaft 332. Camstop 326 defines a cam bore 430 having a diameter greater than thediameter of middle portion 410 and through which middle portion 410extends. However, the diameter of cam bore 430 does not permit frontflange 327 and back flange 329 from traveling through cam bore 430,thereby limiting the relative movement of the sync cam 334 relative tocam stop 326. Middle portion 410, and therefore the distance betweenfront flange 327 and back flange 329, is longer than the thickness ofcam stop 326.

FIG. 5 is a top view of sync cam 334 and shows all three backwarddirection load balancing screws 368 a,b,c extending through the backflange 329. The backward direction load balancing screws 368 a,b,c arethreaded and engage threaded holes defined in the back flange 329.

FIG. 6 shows a cross-sectional view of the sync cam 334 taken alonglines 6-6 in FIG. 5. In the current embodiment, the sync cam 334includes two lobes 620 a and 620 b, which are located on each side of arounded middle section 630. In the current embodiment, sync cam 344includes lobes 640 a,b which are similar to lobes 620 a,b of sync cam334. Also, each lobe 620 a and 620 b extends from the sync cam 334 adistance longer than a distance between the drive shaft 332 and a gatesurface 721 (shown in FIG. 8A) of the gate 320. In the currentembodiment, the lobes 620 a and 620 b include side edges 621 a,b and topedges 623 a,b. A bottom edge 635 extends along the bottom of the synccam 334, including along lobes 620 a,b. Sync cam 334, in the currentembodiment, also includes two threaded forward direction load balancingscrews 335 a and 335 b extending through front nuts 435 a,b and twothreaded forward load balancing holes 622 and 642. Forward loadbalancing hole 622 is defined in lobe 620 a and forward load balancinghole 642 is defined in lobe 620 b; however, this configuration is notmeant to be limiting in terms of the type of mechanism used for forwarddirection load balancing and the number of forward direction loadbalancing mechanisms. Depending on whether or not the type of forwarddirection load balancing mechanism requires a hole or holes, forwarddirection load balancing holes 622 and 642 might or might not benecessary; in some embodiments, more forward direction load balancingholes may be required.

FIG. 7 is a detail view of sync cam 334 extending through the cam stop326 of the gate 320. In the current embodiment, the cam stop 326 issix-sided and made of solid material. Cam stop 326 includes flat edgesat top right side 911, right side 912, left side 914, and top left side915. Additionally, the cam stop 326 includes a rounded top side 916 anda rounded bottom side 913 that approximates the curvature of the gatesurface 721. Although, in the current embodiment, the cam stop 326includes six sides that result in the shape seen in FIG. 7, such adisclosure is not meant to be limiting. Other shapes such as a square,rectangle, triangle, and polygon, among others, may be used for the camstop 326. Moreover, the cam stop 326 need not be of the same shape.Also, in the current embodiment, the cam stop 326 includes cam bore 430as described in the description of FIG. 4. FIG. 7 also shows thepositions of the three backward direction load balancing screws 368a,b,c on the back flange 329

FIG. 8A is a side view of the sleeve 310, gate 320, and drive lines 330and 340. Although in the current embodiment the drive line 340 isconfigured in the same way and includes all of the same components asdrive line 330, the embodiment is not meant to be limiting. Drive line340 may also include or different additional components, and thecomponents in combination described above are not all required. Gate 320includes gate surface 721, which in the current embodiment is made of awelded fabricated stainless steel plate. As shown and described withreference to FIG. 3, when the gate 320 is positioned over at least oneof the perforated openings 315, the material used for gate 320 preventsfluid material from flowing into or out of the interior of the sleeve310 through the at least one perforated opening 315 over which the gate320 is positioned. The shape of gate 320 enables the gate 320 to bemoveable over a portion of the sleeve 310, as seen in FIG. 3, includingat least one of the perforated openings 315 (also seen in FIG. 3).

FIG. 8B is a top view of the sleeve 310, the gate 320, and the driveline 330 from FIG. 8A. The configuration of the drive line 340 issubstantially the same as the configuration of drive line 330 as shownin the current embodiment.

FIGS. 9A-9B show load balancing screw 1010. The load balancing screw1010 can be the backward direction load balancing screws 368 a,b,c or378 a,b,c. In the current embodiment, the load balancing screw 1010include a top end 1012 that connects to the head portion of the loadbalancing screws 1010, a threaded main portion 1011, and a bottom end1014, which is a flat, non-threaded portion. However, the bottom end1014, in the current embodiment, may be threaded or may be configured toend as a sharp point, and the current disclosure is not meant to belimiting. The load balancing screw 1010, in the current embodiment, alsoincludes a self-locking mechanism 1030. The self-locking mechanism 1030includes a piece of plastic material that is packed inside a borethrough the side of the load balancing screw 1010. The self-lockingmechanism 1030 in the current embodiment is not meant to be limiting,and other forms of self-locking may be used or a load balancing screw1010 without a self-locking mechanism 1030 may be used as well.

As can be seen in the current embodiment, the top 1012 of load balancingscrew 1010 is configured with a hexagonal head. However, the currentembodiment is not meant to be limiting and the top 1012 can beconfigured to include other types of heads, such as a slot head, across-head, a torx head, or any other types of head. The top 1012 in thecurrent embodiment is dome shaped, however, other shapes may be used forthe top 1012, such as a low disc with a chamfered outer edge,cylindrical with a rounded top, truss shaped, flat, or any other shape.

As seen in FIG. 10, the drive line 330 includes the sync cam 334 and thedrive shaft 332. The sync cam 334 is moveably positioned relative to thedrive shaft 332. Drive line 340 is configured the same way as the driveline 330 in the current embodiment. Additionally, the drive shaft 332 isthreaded over the entire area in which the sync cam 334 willlongitudinally move along the drive shaft 332, which is cylindrical inthe current embodiment. As can be seen in FIG. 10, the drive shaft 332extends through a bore 1570, which itself extends through the flangedend 134 of the outlet portion 130 to be connected to the machine screwactuator 278 a, which is mounted on the flanged end 134 of the outletportion 130. The drive shaft 332 is connected to the machine screwactuator 278 a by a drive shaft flange 1532 coupled to an actuatorflange 1534 with a plurality of drive shaft flange bolts 1535, thoughthe drive shaft 332 may be connected to the machine screw actuator 278 aby any method in other embodiments. In the current embodiment, to sealthe remainder of the bore 1570 surrounding the drive shaft 332, the bore1570 includes a bearing 1572, a shaft packing seal 1574, a retainerplate 1576, and a plurality of bolts 1578 to hold the retainer plate1576 in place.

Although it appears in the figure that there are two bearings, two shaftpacking seals, and two retainer plates, there is actually only one ofeach because each of these are circular and extend entirely around thedrive shaft 332 to seal the bore 1570, but this is not required. In thecurrent embodiment, the bearing 1572 is made of bronze material, theshaft packing seal 1574 is made of rubber, and the retainer plate 1576and the bolts 1578 are made of metal material. The material used andarrangement for sealing the bore 1570 in the disclosure and the currentembodiment is not meant to be limiting, and one skilled in the art wouldknow of other ways to seal the bore 1570. As can be seen in the currentembodiment, the drive shaft 332 is coupled to the machine screw actuator278 a, which is coupled to the actuator motor 175 (as seen in FIG. 2).In the current embodiment, the machine screw actuator 278 a enables thedrive shaft 332 to rotate, translating rotational movement from theactuator motor 175 to the drive shaft 332. The machine screw actuator278 a, in the current embodiment, includes four actuator spacers 279a,b,c,d, which are coupled to the flanged end 134 of the outlet portion130 and allow the machine screw actuator 278 a to be positioned at adistance from the flanged end 134. Although the present disclosureincludes a machine screw actuator 278 a, such disclosure is not meant tobe limiting and one of skill in the art would recognize other ways toenable to drive shaft 332 to rotate. Additionally, the actuator spacers279 a,b,c,d of the present disclosure are not meant to be limiting, andone of skill in the art would recognize that more or fewer actuatorspacers could be used. Moreover, the machine screw actuator 278 a couldbe separate from the drive shaft 332 or located in a different positionrelative to the sleeve valve 100. More than one of these configurationsin FIG. 10 may be used for the sleeve valve 100. Additionally, in thecurrent embodiment, drive line 340 also includes the same configurationas drive line 330 and the same actuator connection between the driveshaft 342 and the machine screw actuator 278 b as drive line 330 does tomachine screw actuator 278 a. However, the configuration and actuatorarrangement of drive line 340 is not required to be the same as driveline 330 and may be different in various embodiments. Moreover, asdescribed above in FIG. 3, drive line 340 is included in the currentembodiment, but it is not required.

As seen in FIG. 11, a cross-sectional detail view of the interior of thebody cavity portion 140 including the drive line 330, gate 320, andsleeve 310, is provided. In the current embodiment, the flanged end 134of the outlet portion 130 is coupled to flanged end 142 of the bodycavity portion 140.

FIGS. 12A and 12B, show the sync cam 334, the cam stop 326, and thedrive shaft 332 in isolation. In the current embodiment, the forwarddirection load balancing screws 335 a and 335 b of the sync cam 334 areinitially balanced and contacting the gate surface 721 equally, as shownin FIG. 12A. Additionally, in the current embodiment, the forwarddirection load balancing screws 345 a and 345 b of the sync cam 344 areinitially contacting the gate surface 721. In other embodiments, theforward direction load balancing screws 335 a,b and 345 a,b may contactanother structure, including structures mounted on or formed on portionsof the gate 320 or the cam stops 326,346. In the current embodiment,when the forward direction load balancing screws 335 a,b are in contactwith the gate surface 721 and the drive shaft 332 is thereafter turned,the sync cam 334 will move linearly with respect to the drive shaft 332with either the front flange 327 or the back flange 329 moving towardsthe cam stop 326 depending on the direction the drive shafts 332 and 342rotate. This movement takes place because the forward direction loadbalancing screws 335 a,b, when in contact with the gate surface 721,prevent the sync cam 334 from rotating with the drive shaft 332, forcingthe sync cam 334 to move linearly with respect to the drive shaft 332due to the interaction of the threads of the drive shaft 332 with thedrive shaft bore 416. In the current embodiment, the sync cam 344 moveslinearly with respect to the drive shaft 342 in a similar manner.

As will be described in FIGS. 13A-E, during syncing of the currentembodiment, when the front flanges 327,347 of the sync cams 334,344 arebeing synced to the cam stops 326 and 346, respectively, one of thefront flanges 327 or 347 will contact its respective cam stop 326 or 346first. In the current embodiment, in order to have the other frontflange 327 or 347 contact its respective cam stop 326 or 346simultaneously, the forward direction load balancing screws 335 a and335 b (for front flange 327) or 345 a and 345 b (for front flange 347),can be adjusted to enable the non-contacting front flange 327 or 347 tomove linearly along its respective threaded drive shaft 332 or 342. Ascan be seen in FIG. 12B, in the current embodiment, by turning theforward direction load balancing screw 335 a,b, the sync cam 334 rotatesabout the drive shaft 332 and thereby moves linearly along the driveshaft 332 towards or away from the cam stop 326. By screwing forwarddirection load balancing screw 335 a downward within lobe 620 a andscrewing forward direction load balancing screw 335 b upward within lobe620 b, sync cam 334 is rotated clockwise in a direction 1780 and therebymoves in a direction 1750 along the drive shaft 332, as shown in FIG.12B. Screwing forward direction load balancing screw 335 a upward withinlobe 620 a and screwing forward direction load balancing screw 335 bdownward within lobe 620 b rotates sync cam 334 counter-clockwise andthereby moves the sync cam 334 in a direction opposite to direction 1750along the drive shaft 332. In some embodiments, one forward directionload balancing screw 335 a,b must be screwed upward before the otherforward direction load balancing screw 335 b,a can be screwed downwardso that the sync cam 334 can be rotated. In some embodiments, to screwone of the forward direction load balancing screws 335 a,b downward, therespective front nuts 435 a,b must be screwed upward. In theseembodiments, once the sync cam 334 is rotated to the correct position,both forward direction load balancing screws 335 a,b must be screweddownward sufficiently to contact the gate surface 721 to prevent furtherrotation of the sync cam 334. In addition, in some embodiments, thefront nuts 435 a,b may be turned on the forward direction load balancingscrews 335 a,b to place each front nut 435 a,b in contact with therespective lobes 620 a,b to prevent movement of the forward directionload balancing screws 335 a,b once the desired position of the forwarddirection load balancing screws 335 a,b is achieved. In the currentembodiment, the sync cam 344 is moved linearly with respect to the driveshaft 342 in a similar manner. The disclosure described above is notmeant to be limiting, and one of skill in the art would recognize thatthere are other ways such tasks may be performed.

FIGS. 13A, 13B, 13C, 13D, and 13E show a syncing process for the sleevevalve 100. Syncing may be used to ensure that each drive line 330 and340 is applying opening or closing force to the gate 320 at the sametime and with the same degree of force, which will prolong the longevityof each drive line 330 and 340 and the actuator motor 175 and willensure smooth opening and closing of the gate 320. In the currentembodiment, syncing ensures that each drive line 330 and 340 is workingthe same amount by accounting for the machine tolerances in each of thedrive lines 330 and 340, the cam stops 326 and 346, and the splitter274. Syncing may occur during installation, but it can also be achieved,via the inspection ports 190 a and 190 b, later when the sleeve valve100 is assembled. As seen in FIG. 13A, when syncing begins the sync cams334 and 344 may be in a neutral position, meaning the forward directionload balancing screws 335 a,b,345 a,b are all equally screwed down tocontact the gate surface 721 and neither the front flanges 327,347 northe back flanges 329,349 of the sync cams 334,344 are touching the camstops 326,346. However, the sync cams 334 or 344 are not required tobegin in a neutral position.

In the current embodiment, because the drive lines 330,340 are bothconnected to a single actuator motor 175, the drive shafts 332,342 turnat approximately equal speeds and the sync cams 334,344 move linearlytogether along the drive shafts 332,342. In order to sync the sync cams334 and 344 in a front stop position so that both front flanges 327,347contact cam stops 326,346 simultaneously, as shown in FIG. 13C, thefront flanges 327 and 347 are moved linearly together towards respectivecam stops 326,346 so that at least one of the front flanges 327,347contact a cam stop 326 or 346. As shown in FIG. 13B, the front flanges327,347 may not contact the cam stops 326,346 simultaneously prior tosyncing in the front stop position. Once one of the front flanges327,347 contacts a cam stop 326 or 346, the non-contacting front flange327 or 347 is moved linearly along its respective threaded drive shaft332 or 342 so that both front flanges 327,347 contact the cam stops326,346, as can be seen in FIG. 13C, stopping lobes 620 a,b of the synccam 334 and lobes 640 a,b of the sync cam 344 against the gate 320. Atthis point, in FIG. 13C, the sync cams 334 and 344 are synced in thefront stop position.

As seen in FIG. 13D of the current embodiment, to sync each sync cam 334and 344 in the back stop position the back flanges 329,349 are movedlinearly towards the cam stops 326,346 until at least one of the backflanges 329 and 349 contact its respective cam stop 326 or 346. Thebackward direction load balancing screws (368 a,b,c or 378 a,b,c) of thenon-contacting back flange 329 or 349 are then turned to move thebackward direction load balancing screws 368 a,b,c or 378 a,b,c towardsthe non-contacting cam stop 326 or 346 and into contact with thenon-contacting cam stop 326 or 346. The non-contacting back flange 329or 349 thereby effectively contacts its respective cam stop 326 or 346by contacting the backward direction load balancing screws 368 a,b,c or378 a,b,c with the non-contacting cam stop 326 or 346, as shown in FIG.13E. In other embodiments, when the back flanges 329,349 are movedlinearly towards the cam stops 326,346, at least one of the back flanges329 and 349 contacting its respective cam stop 326 or 346 may include atleast one of the cam stops 326 and 346 contacting at least one backwarddirection load balancing screw 368 a, 368 b, 368 c, 378 a, 378 b, or 378c. In these embodiments, syncing the sync cams 334,344 in the back stopposition includes placing each backward direction load balancing screw368 a,b,c and 378 a,b,c in contact with the cam stops 326,346.

In the current embodiment, after syncing in the front stop position andsyncing in the back stop position have occurred, syncing is complete.The disclosure described above is not meant to be limiting, and one ofskill in the art would recognize that there are other ways such tasksmay be performed.

FIGS. 14A, 14B, 14C, 14D, and 14E show how the gate 320 moves inoperation after syncing has occurred. FIG. 14A shows the sync cams 334and 344 in neutral positions (as described in FIG. 13) and the gate 320in a half open position. Neither the gate 320 nor the sync cams 334 and344 must start in this position, and this position is merely describedfor purposes of example. In FIG. 14B of the current embodiment, thedrive shafts 332,342 have been rotated in such a way that the frontflanges 327,347 of the sync cams 334,344 are moved linearly along thedrive shafts 332,342, respectively, toward the cam stops 326 and 346. Ifsyncing in the front stop position has already occurred, then the frontflanges 327 and 347 should contact their respective cam stops 326 and346 at the same time. To ensure that the sync cams 334,344 do not rotateupon rotation of the drive shafts 332,342, the forward direction loadbalancing screws 335 a,b and 345 a,b should be screwed down into contactwith the gate surface 721, though rotation the sync cams 334,344 may beprevented in other manners in other embodiments. As seen in FIG. 14C ofthe current embodiment, after the front flanges 327 and 347 contacttheir respective cam stops 326 and 346 and the drive shafts 332 and 342continue to rotate in the same direction, the gate 320 is moved towardthe open position (where more or all of the perforated openings 315 areexposed). In the open position, the gate 320 allows fluid to flow fromthe inlet 125 through the perforated openings 315 to the outlet 135.FIG. 14C shows the gate 320 in its most open position for the currentembodiment.

In FIG. 14D of the current embodiment, the drive shafts 332 and 342 havebeen rotated in such a way that the back flanges 329 and 349 of the synccams 334 and 344 are moved toward the cam stops 326 and 346. If syncingin the back stop position has already occurred, then the back flanges329 and 349 should contact their respective cam stops 326 and 346 at thesame time (including effective contact between the cam stops 326,346 andthe backward direction load balancing screws 368 a,b,c or 378 a,b,c,respectively). As seen in FIG. 14E of the current embodiment, after thecam stops 326 and 346 contact their respective back flanges 329 and 349(or effectively contact the backward direction load balancing screws 368a,b,c or 378 a,b,c) and the drive shafts 332 and 342 continue to rotatein the same direction, the gate 320 is moved toward the closed position(where more or all of the perforated openings 315 are covered). In theclosed position, the gate 320 restricts fluid flow from the inlet 125through the perforated openings 315 to the outlet 135. FIG. 14E showsthe gate 320 in its most closed position for the current embodiment. Inthese embodiments, space between the cam stops 326,346 and therespective front flanges 327,347 and back flanges 329,349 operates toallow the sync cams 334,344 to “hammer” the gate 320, thereby budgingthe gate 320 from its resting position. With this arrangement, the gate320 may be more easily moved by the sync cams 334,344 than if it werearranged with little or no space between the cam stops 326,346 and therespective front flanges 327,347 and back flanges 329,349 because thesync cams 334,344 gain momentum and hit the respective cam stops 326,346with an inertia that provides additional force than if no inertia waspresent. This “hammer” effect may also dislodge the gate 320 incircumstances where the gate 320 gets stuck on the sleeve 310.

FIG. 15 shows a perspective view of a second embodiment of a valve ofthe present invention in the form of a fixed cone valve 1500. The fixedcone valve 1500 includes a valve body 1510 that has an inner surface1517 (shown in FIG. 18) and an outer surface 1519. The inner surface1517 and the outer surface 1519, as illustrated in the currentembodiment, define a body cavity portion 1540 and an inlet 1525. Thefixed cone valve 1500 also may include a hood 1550 coupled to the bodycavity portion 1540. The hood 1550 includes a hood outer surface 1552and a hood inner surface 1554 (shown in FIG. 18) defining a hood inlet1551 and a hood outlet 1555. The body cavity portion 1540, in thecurrent embodiment, is of an approximately cylindrical shape. The shapeof the body cavity portion 1540 is not limiting and may be other shapes.The body cavity portion 1540 and the hood 1550 in the current embodimentare made of welded fabricated carbon steel plates, although one of skillin the art would recognize that other materials could be used and such adisclosure is not limiting. The body cavity portion 1540 may alsoinclude a flanged end 1524 at the inlet 1525. The fixed cone valve 1500also includes a gate 1820, which is moveable over a portion of the bodycavity portion 1540. The fixed cone valve 1500 also includes a driveassembly 1670 including an actuator motor 1675 in the form of a manualhandwheel 1672 mounted on a motor mount 1543 and drive lines (1830 and1840 in FIG. 18) mounted on drive line mounts 1545,1547, respectively.

FIG. 16 displays a perspective view of the fixed cone valve 1500 withthe hood 1550 removed. FIG. 16 shows that the valve body 1510 includes acone 1650 mounted opposite from the inlet 1525 at a body cavity outlet1527. The cone 1650 is mounted to the body cavity portion 1540 via aplurality of mounting fins 1655 and includes a cone plate 1657 mountedto the cone 1650 by a plurality of fasteners 1659. The cone plate 1657also includes a plurality of hood mounting holes 1651 by which the hood1550 is mounted to the cone 1650. FIG. 16 also shows that the gate 1820has a gate surface 1821.

FIG. 16 also shows drive lines 1830,1840 and gate 1820 in more detail.Drive line 1830 includes drive shaft 1832 and sync cam 1834. Drive line1840 includes drive shaft 1842 and sync cam 1844. Gate 1820 includes camstops 1826,1846 in the form of stop plates, though other cam stops maybe used in other embodiments. Cam stop 1826 includes an adjustment ledge1925, and cam stop 1846 includes adjustment ledge 1945.

As can be seen in the current embodiment, the actuator motor 1675 ismounted to the outer surface 1519 of the body cavity portion 1540 bymotor mount 1543, although the actuator motor 175 may be mounted to anyportion of the fixed cone valve 1500. The actuator motor 1675 isconnected to the drive lines 1830 and 1840 by a splitter 1674, orthree-way gear, and two actuator drive shafts 1676 a and 1676 bextending from the splitter 1674 to two separate machine screw actuators1678 a and 1678 b, where actuator drive shaft 1676 a is attached tomachine screw actuator 1678 a and actuator drive shaft 1676 b isattached to machine screw actuator 1678 b. Splitter 1674 translatesrotational movement from the actuator motor 1675 to the actuator driveshafts 1676 a,b, which translate rotational movement to each machinescrew actuator 1678 a,b, respectively. Machine screw actuator 1678 a ispart of drive line 1830 and machine screw actuator 1678 b is part ofdrive line 1840. In the current embodiment, the machine screw actuators1678 a and 1678 b are Duff-Norton Machine Screw Actuators, model numberDM-9006; however, one of skill in the art would recognize that such adisclosure is not limiting and other types of machines or operationsthat enable the drive shaft 1832 and/or 1842 (described with referenceto FIG. 18) to operate may be used. The drive assembly 1670 is operatedby turning the handwheel 1672. The actuator motor 1675 may also be anelectric motor in alternative embodiments. Drive line mounts 1545 mountmachine screw actuator 1678 a to the gate 1820 and drive line mounts1547 mount machine screw actuator 1678 b to the gate 1820, but themachine screw actuators 1678 a,b may be mounted to the gate 1820 by anyother types or amount of fasteners.

FIG. 17 shows the perspective view of FIG. 16 of the fixed cone valve1500 with the hood 1550 included. The connection between hood 1550 andcone 1650 is shown. Hood 1550 includes a plurality of vanes 1731extending from the hood inner surface 1554 towards a hood mounting post1733. The hood mounting post 1733 extends from a hood mounting plate1735. The hood mounting plate 1735 is coupled to the cone plate 1657 bya plurality of hood mounting fasteners 1737 extending through hoodmounting holes 1651. The hood 1550 may be mounted to the body cavityportion 1540 by any other method in other embodiments.

FIG. 18 provides a cross-sectional view of the fixed cone valve 1500. Inthe current embodiment, material flows into the inlet 1525 through abody cavity defined within the body cavity portion 1540 to the bodycavity outlet 1527 around the cone 1650 and then through the hood 1550to the hood outlet 1555. The gate 1820 is moveable over a portion of thevalve body 1510 and is engageable with the cone 1650. The gate 1820includes a gate sealing rim 1825 and the cone 1650 includes a conesealing rim 1653. When the gate 1820 engages the cone 1650, the gate1820 is placed in a closed position wherein the gate sealing rim 1825contacts and sealably engages the cone sealing rim 1653, creating afluid-tight seal the restricts material from flowing through the bodycavity outlet 1527, effectively closing the body cavity outlet 1527.When the gate 1820 is moved away from the cone 1650, the gate 1820 isplaced in an open position wherein the gate sealing rim 1825 disengagesthe cone sealing rim 1653 and allows material to flow through the bodycavity outlet 1527, effectively opening the body cavity outlet 1527.

FIG. 18 also shows drive lines 1830 and 1840, which are similar in allrespects to drive lines 330 and 340 of the sleeve valve 100. Sync cams1834,1844 are moveably positioned around drive shafts 1832,1842,respectively. Sync cam 1834 includes front flange 1827 and back flange1829, and sync cam 1844 includes front flange 1847 and back flange 1849.Front flange 1827 includes forward direction load balancing screws 1835a,b (1835 a not shown) and front flange 1847 includes forward directionload balancing screws 1845 a,b (1845 b not shown). Drive lines 1830,1840move gate 1820 axially in a similar manner to drive lines 330,340 of thesleeve valve 100, as described with respect to FIG. 14. Additionally,drive lines 1830,1840 are synced in a similar manner to drive lines330,340 of the sleeve valve 100, as described with respect to FIG. 13.

The components of the drive line 1830, in the current embodiment, arenot meant to be limiting. Additional components may be added to thedrive line 1830 and the components in combination described above arenot all required. In the current embodiment, an additional drive line1840 is provided, although it is not required, and is locatedapproximately 180 degrees from drive line 1830, though the drive line1840 may be located relative to the drive line 1830 in any position inother embodiments. Drive line 1840, in the current embodiment, isconfigured in the same way drive line 1830 is configured. Further, camstop 1846, in the current embodiment, is configured in the same way camstop 1826 is configured.

FIG. 19 shows a detail view of the drive line 1830, gate 1820, and bodycavity portion 1540. As seen in FIG. 19, the sync cam 1834, in thecurrent embodiment, includes the front flange 1827, the back flange1829, and a cylindrical middle portion 1910 extending between the frontflange 1827 and the back flange 1829 and through the cam stop 1826,although the components of the sync cam 1834 are not critical. The synccam 1834 also includes backward direction load balancing screws 1868a,b,c (1868 a not shown) extending through the back flange 1829similarly to backward direction load balancing screws 368 a,b,c. In thecurrent embodiment, sync cams 1834,1844 are configured similarly to synccams 334,344 of the sleeve valve 100. Cam stop 1826 defines a cam bore1930 having a diameter greater than the diameter of middle portion 1910and through which middle portion 1910 extends. However, the diameter ofcam bore 1930 does not permit front flange 1827 and back flange 1829from traveling through cam bore 1930, thereby limiting the relativemovement of the sync cam 1834 relative to cam stop 1826. Middle portion1910, and therefore the distance between front flange 1827 and backflange 1829, is longer than the thickness of cam stop 1826.

In addition, FIG. 19 shows the adjustment ledge 1925 of cam stop 1826.Specifically, FIG. 19 shows that forward direction load balancing screws1835 a,b contact adjustment ledge 1925 instead of gate surface 1821.However, adjustment ledge 1925 prevents rotation of sync cam 1834 in asimilar manner to gate surface 721 preventing rotation of sync cam 334of sleeve valve 100. In other embodiments, forward direction loadbalancing screws 1835 a,b may contact gate surface 1821 or any otherstructure that prevents rotation of sync cam 1834.

One should note that conditional language, such as, among others, “can,”“could,” “might,” or “may,” unless specifically stated otherwise, orotherwise understood within the context as used, is generally intendedto convey that certain embodiments include, while other embodiments donot include, certain features, elements and/or steps. Thus, suchconditional language is not generally intended to imply that features,elements and/or steps are in any way required for one or more particularembodiments or that one or more particular embodiments necessarilyinclude logic for deciding, with or without user input or prompting,whether these features, elements and/or steps are included or are to beperformed in any particular embodiment.

It should be emphasized that the above-described embodiments are merelypossible examples of implementations, merely set forth for a clearunderstanding of the principles of the present disclosure. Any processdescriptions or blocks in flow diagrams should be understood asrepresenting modules, segments, or portions of code which include one ormore executable instructions for implementing specific logical functionsor steps in the process, and alternate implementations are included inwhich functions may not be included or executed at all, may be executedout of order from that shown or discussed, including substantiallyconcurrently or in reverse order, depending on the functionalityinvolved, as would be understood by those reasonably skilled in the artof the present disclosure. Many variations and modifications may be madeto the above-described embodiment(s) without departing substantiallyfrom the spirit and principles of the present disclosure. Further, thescope of the present disclosure is intended to cover any and allcombinations and sub-combinations of all elements, features, and aspectsdiscussed above. All such modifications and variations are intended tobe included herein within the scope of the present disclosure, and allpossible claims to individual aspects or combinations of elements orsteps are intended to be supported by the present disclosure.

That which is claimed is:
 1. A valve comprising: a valve body having aninner surface and an outer surface, the inner surface and the outersurface defining an inlet, an outlet, and a body cavity between theinlet and the outlet; a gate movably coupled to the valve body andmoveable over a portion of the valve body at least partially between theinlet and the outlet, the gate including a cam stop; and a driveassembly, the drive assembly including a drive shaft and a sync cam, thesync cam of the drive assembly movably positioned on the drive shaft andslidably positioned relative to the cam stop, the sync cam including atleast one load balancing mechanism.
 2. The valve of claim 1, wherein thesync cam includes two lobes, each lobe extending from the sync cam adistance longer than a distance between the drive shaft and an outersurface of the gate.
 3. The valve of claim 1, wherein the sync camincludes a front flange and a back flange, a distance between the frontflange and the back flange of the sync cam being longer than a thicknessof the cam stop.
 4. The valve of claim 1, wherein the at least one loadbalancing mechanism includes at least one backward direction loadbalancing mechanism.
 5. The valve of claim 4, wherein the at least onebackward direction load balancing mechanism of the drive assemblycomprises three backward direction load balancing screws extendingthrough a back flange of the sync cam.
 6. The valve of claim 1, whereinthe at least one load balancing mechanism includes at least one forwarddirection load balancing mechanism.
 7. The valve of claim 6, wherein theat least one forward direction load balancing mechanism comprises twoforward direction load balancing screws extending through a front flangeof the sync cam.
 8. The valve of claim 1, wherein two cam stops arecoupled to the gate and wherein the drive assembly includes a first synccam coupled to a first drive shaft and a second sync cam coupled to asecond drive shaft.
 9. The valve of claim 8, wherein the first driveshaft and the second drive shaft are positioned on opposite sides of thegate.
 10. The valve of claim 1, wherein the valve body includes a sleevepositioned within the body cavity between the inlet and the outlet, thesleeve including at least one opening, the gate moveable over a portionof the sleeve including the at least one opening.
 11. The valve of claim1, wherein the valve body includes a cone positioned at the outlet ofthe valve body, the gate sealably engageable with the cone.
 12. A methodof syncing a valve comprising: accessing a valve including a valve bodyhaving an inner surface and an outer surface, the inner surface and theouter surface defining an inlet, an outlet, and a body cavity betweenthe inlet and the outlet; a gate coupled to the valve body and moveableover a portion of the valve body at least partially between the inletand the outlet, the gate including a first cam stop and a second camstop; and a drive assembly, the drive assembly including a first synccam movably coupled to a first drive shaft and a second sync cam movablycoupled to a second drive shaft, the first sync cam slidably positionedrelative to the first cam stop, the second sync cam slidably positionedrelative to the second cam stop, the first sync cam including a firstfront flange and a first back flange, the second sync cam including asecond front flange and a second back flange; moving the gate to a frontstop position, wherein the front stop position includes at least one ofthe first front flange and the second front flange in contact with atleast one of the first cam stop and the second cam stop; aligning thefirst front flange in the front stop position to contact the first camstop and the second front flange in the front stop position to contactthe second cam stop; moving the gate to a back stop position, whereinthe back stop position includes at least one of the first back flangeand the second back flange in contact with at least one of the first camstop and the second cam stop; and aligning the first back flange in theback stop position to contact the first cam stop and the second backflange in the back stop position to contact the second cam stop.
 13. Themethod of claim 12, wherein each of the first back flange and the secondback flange includes at least one backward direction load balancingmechanism.
 14. The method of claim 13, wherein the at least one backwarddirection load balancing mechanism of each of the first back flange andthe second back flange is three backward direction load balancingscrews, and wherein aligning the first back flange and the second backflange includes turning at least one backward direction load balancingscrew of at least one of the first back flange and the second backflange.
 15. The method of claim 13, wherein aligning the first backflange and the second back flange includes contacting at least one ofthe at least one backward direction load balancing mechanism of each ofthe first back flange and the second back flange with one of the firstcam stop and the second cam stop.
 16. The method of claim 12, whereineach of the first front flange and the second front flange includes atleast one forward direction load balancing mechanism.
 17. The method ofclaim 16, wherein the first front flange and the second front flangeeach include a first lobe and a second lobe, the first lobe and thesecond lobe each extending from each of the first sync cam and thesecond sync cam a distance between each of the first drive shaft and thesecond drive shaft and an outer surface of the gate, and whereinaligning the first back flange and the second back flange includesstopping the first lobe and the second lobe of each of the first frontflange and the second front flange against the gate.
 18. The method ofclaim 17, wherein aligning the first back flange and the second backflange includes stopping the first lobe and the second lobe of each ofthe first front flange and the second front flange against at least oneadjustment ledge of the gate.
 19. The method of claim 16, wherein the atleast one forward direction load balancing mechanism of each of thefirst front flange and the second front flange is two forward directionload balancing screws, and wherein aligning the first front flange andthe second front flange includes turning at least one forward directionload balancing screw of at least one of the first front flange and thesecond front flange.
 20. The method of claim 19, wherein turning one ofthe two forward direction load balancing screws of the first frontflange moves the first sync cam in a first direction along the firstdrive shaft and wherein turning a second of the two forward directionload balancing screws of the first front flange moves the first sync camin a second direction opposite to the first direction along the firstdrive shaft.
 21. The method of claim 12, wherein the distance betweenthe front flange and the backflange of the first sync cam is longer thana thickness of the first cam stop, and wherein the distance between thefront flange and the back flange of the second sync cam is longer than athickness of the second cam stop.
 22. A method of controlling the flowof a fluid in a pipe system comprising: controlling a valve in the pipesystem, the valve including a valve body having an inner surface and anouter surface, the inner surface and the outer surface defining aninlet, an outlet, and a body cavity between the inlet and the outlet; agate movably coupled to the valve body and moveable over a portion ofthe valve body at least partially between the inlet and the outlet, thegate including a cam stop; and a drive assembly, the drive assemblyincluding a drive shaft and a sync cam on the drive shaft, the sync camof the drive assembly including a front flange and a back flange, thesync cam movably positioned on the drive shaft of the drive assembly andslidably positioned relative to the cam stop, a first gap definedbetween the front flange and the cam stop, a second gap between the backflange and the cam stop, the drive assembly including at least one loadbalancing mechanism; moving the sync cam in a first direction to a frontstop position, wherein the front stop position reduces the first gap;and moving the gate in the first direction to allow fluid to flow fromthe inlet to the outlet.
 23. The method of claim 22, wherein moving thegate includes moving the sync cam along the drive shaft.
 24. The methodof claim 22, wherein the front stop position includes at least one frontflange of at least one sync cam in contact with at least one cam stop.25. The method of claim 22, wherein the front flange of the sync camincludes a first lobe and a second lobe, the first lobe and the secondlobe stopped against the gate.
 26. The method of claim 22, wherein theat least one load balancing mechanism includes at least one forwarddirection load balancing screw in the sync cam.
 27. The method of claim22, wherein the at least one load balancing mechanism includes at leastone backward direction load balancing screw in the sync cam.
 28. Themethod of claim 22, wherein the gate includes a second cam stop andwherein the drive assembly includes a second drive shaft and a secondsync cam, the second sync cam of the drive assembly including a frontflange and a back flange, the second sync cam movably positioned on thesecond drive shaft of the drive assembly and slidably positionedrelative to the second cam stop.
 29. The method of claim 28, wherein thesecond drive shaft is positioned on an opposite side of the gate fromthe first drive shaft.
 30. The method of claim 22, further comprising:moving the sync cam in a second direction to a back stop position,wherein the back stop position reduces the second gap; and moving thegate in the second direction over the valve body to restrict fluid flowfrom the inlet to the outlet.
 31. The method of claim 30, wherein movingthe gate in the second direction over the valve body to restrict fluidflow from the inlet to the outlet includes moving the sync cam along thedrive shaft.
 32. The method of claim 30, wherein the valve body includesa cone positioned at the outlet of the valve body; moving the gatefurther in the first direction includes moving the gate away from asealing rim of the cone; and moving the gate further in the seconddirection includes moving the gate towards the sealing rim of the coneand into sealing engagement with the cone.
 33. The method of claim 30,wherein: the valve body includes a sleeve positioned within the bodycavity between the inlet and the outlet, the sleeve including at leastone opening; moving the gate further in the first direction includesmoving the gate over the sleeve to to uncover the at least one opening;and moving the gate further in the second direction includes moving thegate over the sleeve to cover the at least one opening.